CN1011528B - Hydraulic system - Google Patents
Hydraulic systemInfo
- Publication number
- CN1011528B CN1011528B CN87102639A CN87102639A CN1011528B CN 1011528 B CN1011528 B CN 1011528B CN 87102639 A CN87102639 A CN 87102639A CN 87102639 A CN87102639 A CN 87102639A CN 1011528 B CN1011528 B CN 1011528B
- Authority
- CN
- China
- Prior art keywords
- pressure
- circuit
- oil hydraulic
- main oil
- boost
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000001105 regulatory effect Effects 0.000 claims description 11
- 239000012530 fluid Substances 0.000 abstract description 15
- 239000000945 filler Substances 0.000 description 9
- 230000007935 neutral effect Effects 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 5
- 239000002828 fuel tank Substances 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4008—Control of circuit pressure
- F16H61/4026—Control of low pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/68—Inputs being a function of gearing status
- F16H2059/6838—Sensing gearing status of hydrostatic transmissions
- F16H2059/6861—Sensing gearing status of hydrostatic transmissions the pressures, e.g. high, low or differential pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/421—Motor capacity control by electro-hydraulic control means, e.g. using solenoid valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Motor Power Transmission Devices (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The hydraulic system according to the present invention includes: the hydraulic pump and the hydraulic motor are connected with a pair of closed main hydraulic circuits; a booster circuit for supplying the hydraulic fluid output from the booster pump to a low-pressure side of the main hydraulic circuit; a pilot control circuit for leading out pilot control pressure from the high-pressure side of the main hydraulic circuit to make the auxiliary actuator work; the pressure boost regulator increases the pressure of the boost circuit only when the pressure difference between the two main hydraulic circuits is lower than a set value. It can change the pressure boost according to the pressure difference between two main hydraulic circuits.
Description
The present invention relates generally to and can use in hydrostatic gearbox and hydraulic pressure automatic transmission case transmission devices such as (HST, HMT), also the hydraulic system that can use in various hydraulic machineries field.
The hydraulic system that adopts in the transmission devices such as above-mentioned HST, HMT generally is linked to be closed-circuit system by the paired main oil hydraulic circuit that the oil hydraulic motor of the oil hydraulic pump of input side and outlet side constitutes.Above-mentioned oil hydraulic pump and oil hydraulic motor all are variable types, can carry out stepless change, and in this hydraulic system, the hydraulic pilot control mode is mostly adopted in the control of the variable of oil hydraulic pump or oil hydraulic motor.This control mode changes the swash plate angle of oil hydraulic pump or oil hydraulic motor and offset of cylinder tube or the like with the servomechanism that is equipped with hydraulic actuator.As its hydraulic power, need to be equipped with special service pump.
, be provided with such service pump after, brought number of components to increase, problems such as complex structure.Therefore, consider in above-mentioned main oil hydraulic circuit, guiding valve to be set, draw the control oil pressure that hydraulic pressure is used as Variable Control by the high pressure side of main oil hydraulic circuit, thereby save above-mentioned service pump.But, when using this hydraulic system in transmission device, when being in neutral or near position it, the pressure in above-mentioned two kinds of oil hydraulic circuits has all dropped to the supercharging that topping up is used, under common imposing a condition, can not make the hydraulic actuator work of controlled variable.In this hydraulic system, in order to prevent to produce air pocket, the low voltage side of supplying with main oil hydraulic circuit from the pressure oil of suction booster output by boost-up circuit at the oil inlet end of oil hydraulic pump.To prevent that air pocket from being under the situation of purpose, this supercharging is set in 5 kilograms per centimeter usually only
2Below., the Variable Control of oil hydraulic pump and oil hydraulic motor but needs higher pressure, for example 20 kilograms per centimeter must be arranged
2Above pressure.Therefore have only by supercharging being set to higher value and just can carry out such control.But, like this, no matter which side is following time of common operating condition under high pressure in above-mentioned main oil hydraulic circuit, and promptly being in does not need to make under the working order of Variable Control element work with supercharging, to make the too much power of suction booster consumption, cause a large amount of losses of energy.
Purpose of the present invention will address this problem exactly.
The hydraulic system of original technology of service pump is set, owing to number of components increases, complex structure, the power supply that drives service pump is necessary, therefore the problem that exists the integral energy conversion efficiency to reduce.For head it off, according to the present invention, do not use service pump fully, only utilize system pressure, just can carry out volume controlled, can improve the integral energy conversion efficiency.
The present invention a kind ofly can realize above-mentioned purpose, changes the hydraulic system of supercharging according to the pressure reduction between two main oil hydraulic circuits.The feature of hydraulic system of the present invention is to possess following oil hydraulic circuit and device: oil hydraulic pump and oil hydraulic motor continue into the paired main oil hydraulic circuit of closed circuit state; The pressure oil of suction booster output is supplied with the boost-up circuit of main oil hydraulic circuit low voltage side; Draw the guide from the high pressure side of main oil hydraulic circuit and control pressure, make guide's control loop of secondary actuator work; Just improve the pressurized regulating device of boost-up circuit pressure when only the pressure reduction between two main oil hydraulic circuits is lower than setting value.
Hydraulic system by means of this structure, the pressure height of the main oil hydraulic circuit of which side no matter, as long as the pressure reduction between two main oil hydraulic circuits is higher than setting value, just can draw the guide and control pressure, control the secondary actuator work of carrying out Variable Control that makes of pressing by this guide from high-tension side main oil hydraulic circuit.Simultaneously, supercharging remains on the low pressure values of regulation.
On the other hand, when the pressure reduction of two main oil hydraulic circuits is lower than setting value, can be by means of pressurized regulating device be used for improving supercharging.Therefore, above-mentioned secondary actuator just can be compressed into capable work as guide's control with supercharging or the system pressure that maintains more than the supercharging.
Like this, neither service pump need be set, the power consumption that needn't too improve suction booster again just can make the secondary actuator proper functioning.
The 1st figure is the system specialization figure of expression one embodiment of the present of invention.The 2nd figure is the sectional drawing of pressurized regulating device among the same embodiment of expression.The 3rd figure is the system specialization figure of another embodiment of the present invention.
Each label representative among the figure:
1 ... hydraulic system
3 ... oil hydraulic pump
5 ... oil hydraulic motor
6,7 ... main oil hydraulic circuit
9,10 ... secondary actuator
11 ... guide's control loop
13 ... suction booster
16 ... boost-up circuit
17 ... pressurized regulating device
21 ... relief valve
22 ... executive component
23 ... high selector relay
70 ... pressurized regulating device
Below, with reference to the 1st figure and the 2nd figure, one embodiment of the present of invention are described.
The 1st figure has roughly represented the hydraulic system 1 that adopted in transmission devices such as HST, HMT.
This hydraulic system 1 is the paired main oil hydraulic circuit 6,7 of oil hydraulic motor 5 usefulness of oil hydraulic pump 3 that is driven by motor 2 and driving ambulation single wheel 4 usefulness to be connected into closed circuit state form.Oil hydraulic pump 3 and oil hydraulic motor 5 be configured to variable displacement, by means of the thrust of secondary actuator 9,10, the eccentric position of the oil hydraulic cylinder cylinder barrel that does not show among the change figure etc. can make discharge capacity in the stepless variation of positive and negative both direction.Secondary actuator the 9, the 10th carries out work with hydraulic pressure as power source.Be connected with above-mentioned two main oil hydraulic circuits 6,7 by guide's control loop 11, promptly, guide's control loop 11 is communicated with two main oil hydraulic circuits 6,7 by shuttle valve 12, so the hydraulic pressure of main oil hydraulic circuit 6 or 7 mesohigh sides is just supplied with secondary actuator 9,10 as power source by this guide's control loop 11.In addition, in order to prevent to produce air pocket, the pressure oil of suction booster 13 outputs is supplied with two main oil hydraulic circuits by the boost-up circuit that one-way valve 14,15 is housed after branch in the oil-feed side of oil hydraulic pump 3.
And, can change the pressure of this boost-up circuit by pressurized regulating device 17.Pressurized regulating device 17 only is lower than setting value (15 kilograms per centimeter for example at the pressure reduction of 6,7 of main oil hydraulic circuits
2) time, just the pressure of boost-up circuit 16 is brought up to the value that sets, it is equipped with the relief valve 21 that is connected with boost-up circuit 16, the overflow of this relief valve 21 is set be pressed in the executive component 22 that high and low two-stage changes, and according to the high selector relay 23 of 6,7 pressure reduction control actuating component of main oil hydraulic circuit, 22 work.
Introduce the structure of pressurized regulating device below in detail.The 1st valve body 24 is sealedly connected on the side of the 2nd valve body 25, is equipped with in the 1st valve body 24 in relief valve 21 and executive component 22, the 2 valve bodies 25 high selector relay 23 is housed.One end of the 1st valve body 24 is equipped with the loop of connecting with boost-up circuit 16 hydraulic fluid port 26 that continues, there is the small-diameter hole 27 that is communicated with the continuous hydraulic fluid port 26 in loop its inside, medium caliber hole 28 and heavy caliber hole 29 offer the fuel tank hydraulic fluid port 31 that heavy caliber hole 29 is communicated with fuel tank 30 on its wall.Relief valve 21 forms valve seat 32 at the inner end of above-mentioned small-diameter hole 27, and insertion can by being contained in the elastic force of the spring 34 in the heavy caliber hole, be pressed on the valve seat 32 this poppet valve 33 along the poppet valve 33 of axis m direction slip in medium caliber hole 28 simultaneously.The axis of executive component 22 is consistent with the axis m of poppet valve, be provided with fixed piston 36 with the front end that is threaded in the fixed tube 35 on the 2nd valve body 25, periphery at fixed piston 36 is with the columnar spring retainer 37 that can slide, the periphery of spring retainer 37 has location stop flange 37a, pressure adjusting spring 34 just is contained between location stop flange 37a and the poppet valve 33, between location stop flange 37a and the 2nd valve body 25 executive component spring 38 is housed then.Form pressure chamber 39 between the end face of the internal surface of this external spring retainer 37 and fixed piston 36, the fluid passage 41 by in the fixed tube 35 makes pressure chamber 39 be communicated with the oil outlet 42 of high selector relay 23.High selector relay 23 is respectively arranged with the pressure oil filler opening 43 that is connected with each main oil hydraulic circuit 6,7 at the two ends of the 2nd valve body 25,44, and there are cylindrical hole 45 and heavy caliber hole 46 in its inside, and the guiding valve 47 that can slide on axis n direction freely is housed in cylindrical hole 45.Guiding valve 47 is sealed and matched in cylindrical hole 45, in its periphery the 1st, the 2nd circular groove 48,49 is arranged, and its an end 47a is positioned at heavy caliber hole 46.And, at end 47a flange sections 51 and thread section 52 are arranged, acorn nut 53 is housed on thread section 52, in addition, in heavy caliber hole 46, be provided with and make guiding valve 47 flexibly remain on guiding valve retaining mechanism 54 on the represented neutral position of the 2nd figure.When the hydraulic difference that acts on guiding valve 47 two ends, the pressure reduction that promptly is connected the main oil hydraulic circuit 6,7 on the pressure input hydraulic fluid port 43,44 is (15 kilograms per centimeter for example in setting range
2In) time, guiding valve retaining mechanism 54 remains on the neutral position guiding valve 47.This guiding valve retaining mechanism is made of following key element: paired location prevent surface 55,56 in valve body 25; Can between two location prevent surfaces 55,56, move, in pairs the movable member 57,58 of configuration; Be pressed on the movable member 57,58 both separated in the opposite direction, and respectively with the spring 59 of corresponding location prevent surface 55,56 Elastic Contact; Be arranged on guiding valve 47 1 ends, when guiding valve 47 when some directions move, just the some pressure planes 61,62 in two movable members 57,58 to the direction pushing of leaving corresponding location prevent surface 55,56.Above-mentioned movable member 57,58 is cup-shaped, is enclosed within on the periphery of guiding valve 47 1 ends, can slide, and at open end flange 57a and 58a is arranged.The exterior edge face of flange 57a, 58a is pressed on the prevent surface 55,56 of location, and interior edge face withstands on the spring 59.The pressure plane 61 of pushing movable member 57 is formed by the end face of the acorn nut 53 of guiding valve 47, and the pressure plane 62 of pushing movable member 58 is formed by lip part 51.In addition, in the 2nd valve body 25, also be provided with: the oil outlet 42 that is communicated with the 1st circular groove 48 of guiding valve 47; The oil drain out 63 that the 2nd circular groove 49 is communicated with above-mentioned fuel tank hydraulic fluid port 31; The groove 64 that the 1st, 2 circular grooves are communicated with; When below guiding valve 47 is in figure, moving, the 1st commutation hydraulic fluid port 65 that the 1st pressure oil filler opening 43 is communicated with the 1st circular groove 48; When above guiding valve 47 is in figure, moving, the 2nd commutation hydraulic fluid port 66 that the 2nd pressure oil filler opening 44 is communicated with the 1st circular groove.
This embodiment's working condition below is described,
At first, under the situation that vehicle is advanced, the 1st main oil hydraulic circuit 6 is high pressure, and the 2nd main oil hydraulic circuit 7 is a low pressure.At this moment, by pressure oil filler opening 43 input, act on the hydraulic pressure of guiding valve 47 upper ends, and by 44 inputs of pressure oil filler opening, the difference that acts on the hydraulic pressure of guiding valve 47 lower ends surpasses the setting of guiding valve retaining mechanism 54 and presses.As a result, guiding valve 47 overcomes the elastic force of guiding valve retaining mechanism 54 medi-springs 59, makes movable member 57 leave location prevent surface 55, and move the below in figure.Therefore the 1st, 2 circular grooves 48,49 have been cut off, the 1st pressure oil filler opening 43 is communicated with the 1st commutation hydraulic fluid port 65, the high pressure oil of the 1st main oil hydraulic circuit 6 flows in the 1st circular groove 48 by the 1st pressure oil filler opening 43 and the 1st commutation hydraulic fluid port 65, then, the pressure oil that flows into the 1st circular groove 48 enters the pressure chamber 39 of executive component 22 from oil outlet 42, the spring retainer 37 of executive component 22 overcomes the elastic force of executive component spring 38, retreats and remain on valve body 25 to contact or approaching position.Thereby the pressure adjusting spring 34 of relief valve 21 remains on the state of elongation, and relief valve 21 will be according to the setting value of low voltage side (5 kilograms per centimeter for example
2) open and close.Therefore, the supercharging by boost-up circuit 16 supply low voltage side master oil hydraulic circuits 7 maintains low pressure setting value (5 kilograms per centimeter
2) produce to prevent air pocket.In this case, because main oil hydraulic circuit 6 on high-tension side hydraulic pressure are supplied with Variable Control secondary actuator 9,10 by guide's control loop 11, thus irrelevant with supercharging, can make secondary actuator 9,10 work.
If the discharge capacity of oil hydraulic pump 3 and oil hydraulic motor 5 is transferred to neutral gear position from the situation that vehicle advances, the pressure of the 1st main oil hydraulic circuit 6 descends so.And drop to for example 20 kilograms per centimeter when this hydraulic pressure
2The time, the pressure reduction that main oil hydraulic circuit is 6,7 just reduces to 15 kilograms per centimeter
2Therefore, the guiding valve 47 of high selector relay 23 is because the effect of guiding valve retaining mechanism 54 is returned to the neutral position.The result, two commutation hydraulic fluid ports 65,66 are closed by guiding valve 47, the 1st circular groove 48 and the 2nd circular groove 49 become connected state by groove 64, and the pressure chamber 39 of executive component 22 connects with fuel tank hydraulic fluid port 31 by oil outlet 42, two circular grooves 48,49 and oil drain out 63.So retainer of the spring 37 advances to the position that the elastic force of executive component spring 38 and pressure adjusting spring 34 balances each other, the i.e. position that solid line is represented among the 2nd figure.Like this, the shorten length of pressure adjusting spring 34, the cracking pressure of relief valve 21 is elevated to high pressure side setting value (20 kilograms per centimeter for example
2).Therefore, when gearbox hung on the neutral or turn round in its vicinity, promptly the pressure reduction of 6,7 of two main oil hydraulic circuits was lower than 15 kilograms per centimeter
2Scope the time, 20 kilograms per centimeter are just brought up in supercharging
2, keep system pressure in 20 kilograms per centimeter
2More than.Thereby make control discharge capacity secondary actuator 9,10 in this case also can proper functioning.
When discharge capacity further when above neutral is transferred to negative direction and is made vehicle rollback, the pressure of the 2nd main oil hydraulic circuit 7 rises.Then, the pressure reduction when 6,7 of two main oil hydraulic circuits surpasses 15 kilograms per centimeter
2The time, the pressure reduction that acts on the hydraulic pressure of guiding valve 47 upper ends and the hydraulic pressure that acts on guiding valve 47 lower ends surpasses the setting pressure that guiding valve guarantees mechanism 54 again.The result, guiding valve 47 overcomes the elastic force of the spring 59 of this guiding valve retaining mechanism 54, make movable member 58 leave location prevent surface 56, move the top in figure, disconnect the 1st, 2 circular grooves 48,49, simultaneously the 2nd pressure oil filler opening 44 is communicated with the 2nd commutation hydraulic fluid port 66, the high pressure oil in the 2nd main oil hydraulic circuit 7 is input to the 1st circular groove 48 by the 2nd pressure oil filler opening 44 and the 2nd commutation hydraulic fluid port 66.And the pressure oil that is input to the 1st circular groove 48 enters into the pressure chamber of executive component 22 from oil outlet 42, make the spring retainer 37 of this executive component overcome the elastic force of executive component spring 38, fall back on and remain on valve body 25 and contact or approaching position, Regulation spring 34 extends once more, makes the supercharging of supplying with low voltage side master oil hydraulic circuit 6 be reduced to 5 kilograms per centimeter
2At this moment, owing to be in the secondary actuator 9,10 of the hydraulic pressure of the main oil hydraulic circuit 7 under the high pressure, make secondary actuator 9,10 work and irrelevant with supercharging by guide's control loop 11 supply controlled variable.
Like this, fully any service pump need not be set, just can make control discharge capacity secondary actuator 9,10 proper functioning.And, as long as being in, the pressure reduction of two main oil hydraulic circuits 6,7 is higher than 15 kilograms per centimeter
2Scope under when turning round, because supercharging still maintains necessary minimum (5 kilograms per centimeter
2), the situation of the power consumption of suction booster 13 can not take place unnecessarily to increase.And, the compression area of the elastic force of the dead band width by suitable selection high selector relay 23, the pressure adjusting spring 34 of relief valve 21 and executive component spring 38 or the pressure chamber 39 of executive component 22, just can do various settings, applicable to various oil hydraulic circuits to supercharging and its pressure changing condition.
The present invention is not limited to the above embodiments certainly, and for example, the represented hydraulic system of the 3rd figure also can obtain the basic effect same with above-mentioned situation.In the pressurized regulating device 70 of the 3rd figure, be set in for example 20 kilograms per centimeter opening valve setting pressure
2High-pressure overflow valve 71 and drive valve and set to press and be set in for example 5 kilograms per centimeter
2Low pressure relief valve 72 be connected on the boost-up circuit 16 by stop valve 73,74 respectively, simultaneously differential pressure pickup 75 is set 6,7 of main oil hydraulic circuits.The signal of differential pressure pickup 75 is input to stop valve control gear 76,, opens and closes stop valve 73,74 selectively by this control gear 76.Be control gear 76 at differential pressure pickup 75 detected pressure reduction during greater than setting value, only open stop valve 74, low pressure relief valve 72 and boost-up circuit 16 are connected, when above-mentioned pressure reduction is lower than setting value, only open another stop valve 73, high-pressure overflow valve 71 and boost-up circuit are connected.Among the 3rd figure, parts same as the previously described embodiments all are marked with identical label, have no longer illustrated.
In addition, the setting value of enumerating among the above embodiment only is an example, in not breaking away from design philosophy scope of the present invention, various versions can be arranged.
The present invention can provide the hydraulic system that has the following advantages, promptly owing to have said structure, do not need service pump fully, only utilize system pressure just can make the secondary actuator work of the displacement variation of control oil hydraulic pump and oil hydraulic motor at any time as required, therefore can not bring unnecessary load yet, increase power consumption to suction booster.
Claims (2)
1, a kind of hydraulic system, comprise: oil hydraulic pump and motor connect into the paired main oil hydraulic circuit of closed circuit state, a pair of one-way valve between main oil hydraulic circuit links to each other with boost-up circuit, be connected a shuttle valve between the main oil hydraulic circuit, the pressure oil of suction booster output is supplied with the boost-up circuit of main oil hydraulic circuit low voltage side, be connected in relief valve and selector valve on the boost-up circuit, it is characterized in that, system comprises that also drawing the guide from the high pressure side of main oil hydraulic circuit controls pressure, make guide's control loop of secondary actuator work, just improve the pressurized regulating device of boost-up circuit pressure when only the pressure reduction between two main oil hydraulic circuits is lower than setting value.
2, hydraulic system as claimed in claim 1, it is characterized in that, described pressurized regulating device has following parts: be connected on the relief valve on the boost-up circuit, the executive component that the holding position of the pressure adjusting spring of this relief valve can be changed in locations of high pressure and locations of low pressure two-stage, draw pressure oil from the high pressure side of main oil hydraulic circuit and supply with this executive component, make this executive component remain on locations of low pressure in advance, when the pressure reduction between main oil hydraulic circuit is lower than setting value, block the supply of above-mentioned pressure oil, make the high selector relay of this executive component in locations of high pressure work.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP136969/86 | 1986-06-11 | ||
| JP61136969A JPS62292958A (en) | 1986-06-11 | 1986-06-11 | Hydraulic system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN87102639A CN87102639A (en) | 1987-12-23 |
| CN1011528B true CN1011528B (en) | 1991-02-06 |
Family
ID=15187713
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN87102639A Expired CN1011528B (en) | 1986-06-11 | 1987-04-09 | Hydraulic system |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US4779417A (en) |
| EP (1) | EP0249154B1 (en) |
| JP (1) | JPS62292958A (en) |
| KR (2) | KR880000704A (en) |
| CN (1) | CN1011528B (en) |
| DE (1) | DE3762276D1 (en) |
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| CN106537000B (en) | 2014-07-09 | 2018-06-15 | 加特可株式会社 | The control device of contiuously variable transmission |
| DE102014214441B4 (en) | 2014-07-23 | 2016-02-18 | Danfoss Power Solutions Gmbh & Co. Ohg | Method and arrangement for decelerating a hydrostatic drive |
| CN105443462A (en) * | 2014-08-12 | 2016-03-30 | 安钛医疗设备股份有限公司 | Two-way output hybrid hydraulic power system |
| FR3033529B1 (en) * | 2015-03-13 | 2018-05-18 | Poclain Hydraulics Industrie | HYDRAULIC ASSISTANCE DEVICE ON VEHICLE AND METHOD FOR EMPTYING SUCH A DEVICE |
| DE102015006321A1 (en) * | 2015-05-16 | 2016-11-17 | Hydac System Gmbh | Hydrostatic drive |
| CN105201940A (en) * | 2015-10-22 | 2015-12-30 | 太原科技大学 | Novel hydraulic direct-driven system based on single side pressure feedback |
| CN106763743B (en) * | 2016-12-26 | 2019-02-12 | 潍柴动力股份有限公司 | A kind of mobile gear-shifting control method of hydrostatic transmissions and system |
| CN106827648A (en) * | 2017-04-18 | 2017-06-13 | 河海大学常州校区 | A kind of hydraulic/mechanical combination drive servo-press transmission system |
| CN107842537B (en) * | 2017-12-11 | 2024-04-30 | 江苏徐工工程机械研究院有限公司 | End cover assembly, hydraulic equipment and engineering machinery |
| CN110778552B (en) * | 2019-09-30 | 2021-06-01 | 长沙中联重科环境产业有限公司 | Closed hydraulic system, exhaust method of closed hydraulic system and washing and sweeping vehicle |
| CN110953338B (en) * | 2019-12-03 | 2021-04-20 | 航天重型工程装备有限公司 | Speed stabilizing control system |
| IT202100000953A1 (en) * | 2021-01-20 | 2022-07-20 | Faymonville Distrib Ag | METHOD AND CLOSED-CIRCUIT HYDRAULIC MOTORIZATION SYSTEM FOR CONTROLLING THE MOVEMENT OF A TRANSPORT VEHICLE |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3186162A (en) * | 1963-09-10 | 1965-06-01 | Gen Mecanique Applique S I G M | Prime mover systems |
| FR1411401A (en) * | 1963-10-12 | 1965-09-17 | Hako Werke Hans Koch & Sohn | Hydrostatic propulsion system for working machines |
| FR1561808A (en) * | 1967-06-13 | 1969-03-28 | ||
| DE1751471A1 (en) * | 1968-06-05 | 1971-05-19 | Bosch Gmbh Robert | Control and regulating device for a hydrostatic transmission |
| US3747350A (en) * | 1972-02-03 | 1973-07-24 | Sperry Rand Corp | Power transmission |
| DE2231421C3 (en) * | 1972-06-27 | 1981-04-23 | Robert Bosch Gmbh, 7000 Stuttgart | Hydrostatic transmission |
| SU568754A1 (en) * | 1975-04-14 | 1977-08-15 | Предприятие П/Я А-3243 | Positive displacement hydraulic drive |
| DE2644128A1 (en) * | 1976-09-30 | 1978-04-06 | Bosch Gmbh Robert | CONTROL DEVICE FOR A HYDROSTATIC TRANSMISSION |
| JPS5876853U (en) * | 1981-11-19 | 1983-05-24 | 株式会社小松製作所 | hydraulic drive |
-
1986
- 1986-06-11 JP JP61136969A patent/JPS62292958A/en active Pending
-
1987
- 1987-04-09 CN CN87102639A patent/CN1011528B/en not_active Expired
- 1987-06-04 EP EP87108107A patent/EP0249154B1/en not_active Expired - Lifetime
- 1987-06-04 DE DE8787108107T patent/DE3762276D1/en not_active Expired - Fee Related
- 1987-06-05 US US07/058,372 patent/US4779417A/en not_active Expired - Fee Related
- 1987-06-08 KR KR870005770A patent/KR880000704A/en not_active IP Right Cessation
- 1987-06-08 KR KR1019870005770Q patent/KR910007261B1/en active
Also Published As
| Publication number | Publication date |
|---|---|
| DE3762276D1 (en) | 1990-05-17 |
| EP0249154A1 (en) | 1987-12-16 |
| CN87102639A (en) | 1987-12-23 |
| US4779417A (en) | 1988-10-25 |
| KR910007261B1 (en) | 1991-09-24 |
| KR880000704A (en) | 1988-03-28 |
| EP0249154B1 (en) | 1990-04-11 |
| JPS62292958A (en) | 1987-12-19 |
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